EP0635658A2 - Transmission à trains épicycloidaux équipée d'un limitateur de couple et son application dans des outils à main - Google Patents

Transmission à trains épicycloidaux équipée d'un limitateur de couple et son application dans des outils à main Download PDF

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Publication number
EP0635658A2
EP0635658A2 EP94110238A EP94110238A EP0635658A2 EP 0635658 A2 EP0635658 A2 EP 0635658A2 EP 94110238 A EP94110238 A EP 94110238A EP 94110238 A EP94110238 A EP 94110238A EP 0635658 A2 EP0635658 A2 EP 0635658A2
Authority
EP
European Patent Office
Prior art keywords
gear
ring gear
ring
transmission according
protective plate
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP94110238A
Other languages
German (de)
English (en)
Other versions
EP0635658A3 (fr
EP0635658B1 (fr
Inventor
Bernd Enzmann
Hansjörg Maus
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
IMS Morat Soehne GmbH
Original Assignee
IMS Morat Soehne GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by IMS Morat Soehne GmbH filed Critical IMS Morat Soehne GmbH
Publication of EP0635658A2 publication Critical patent/EP0635658A2/fr
Publication of EP0635658A3 publication Critical patent/EP0635658A3/fr
Application granted granted Critical
Publication of EP0635658B1 publication Critical patent/EP0635658B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B23/00—Details of, or accessories for, spanners, wrenches, screwdrivers
    • B25B23/14—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers
    • B25B23/141—Mechanical overload release couplings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
    • F16D7/04—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type
    • F16D7/042—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type with at least one part moving axially between engagement and disengagement
    • F16D7/044—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type with at least one part moving axially between engagement and disengagement the axially moving part being coaxial with the rotation, e.g. a gear with face teeth
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/46—Systems consisting of a plurality of gear trains each with orbital gears, i.e. systems having three or more central gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H35/00—Gearings or mechanisms with other special functional features
    • F16H35/10—Arrangements or devices for absorbing overload or preventing damage by overload

Definitions

  • the invention relates to a transmission with the features of the preamble of claim 1 and its use.
  • Such a transmission is already used today in an accumulator-driven electric screwdriver, a so-called cordless screwdriver.
  • this accumulator-driven electric screwdriver the number of revolutions provided by a motor on a drive shaft is reduced via an epicyclic gear (planetary gear) to an output shaft that holds a screw chuck.
  • a torque limiting device in the form of an overload clutch is provided to adapt the cordless screwdriver to different loads. This torque limiting device can be used to tighten screws with a specified torque.
  • the overload clutch has a ring gear which surrounds the last epicyclic gear stage and which contains an internal toothing which engages with the planet gear of the last stage.
  • a compression spring which axially presses the ring gear against a stop wall by means of a pressure ring such that it is held in a rotationally fixed manner by friction locking, as long as a predetermined torque load has not been reached.
  • the predetermined torque load is exceeded, the pressure force on the ring gear generated by the spring device is no longer sufficient, so that the ring gear is released for rotation and begins to slip.
  • the ring gear is provided on the end face on the side facing the compression spring with trough-shaped depressions in which, in the event that a predetermined torque load has not yet been reached, balls of a ball ring are seated under pressure from the compression spring. If, on the other hand, the specified torque load is exceeded, these balls slide out of the trough-shaped depressions, so that the ring gear begins to rotate and a torque limitation is thereby set.
  • metal powder must first be placed in a mold and the pulverulent substance compressed under pressure and / or temperature at a temperature which is not below the melting point of the mixture of substances. This causes the goods to melt and bake together at the grain boundaries of the metal powder.
  • the molded article to be produced is presintered in a first step and sintered up in a second step for maximum compression.
  • this known transmission is also characterized by relatively loud and therefore unpleasant running noises out.
  • Gears of electrically driven tools are also known from DE 41 23 349 C1, DE 37 42 952 A1 and DE 27 26 818 B2.
  • DE 41 23 349 C1 describes a screwdriver with a gear which has a planetary gear with a ring gear and an overload clutch coupled to it.
  • the overload clutch consists of a compression spring which acts axially on the end face of the second ring gear of the planetary gear.
  • a so-called roller mount is provided between the compression spring and the end face of the second ring gear, for accommodating rollers arranged radially to one another, and balls lying between these rollers, which are pressed into the spaces between the rollers by the compression spring via an axial disk. When a certain limit torque is reached, the balls move out of their position between the rollers, so that a counter-torque is transmitted to the ring gear of the transmission, thus ensuring effective overload protection.
  • DE 37 42 952 A1 describes a motor-driven machine with variable torque setting with a motor and a planetary gear that drives a work spindle.
  • the planetary gear comprises a ring gear which is rotatably mounted and, when an adjustable limit torque is exceeded, against the action of a spring force, which actuates a motor switch.
  • the spring force is provided by a torsion bar.
  • the overload device in DE 27 26 818 B2 of a transmission for an electrically driven tool has, similar to the transmission in DE 41 23 349 C1, coupling balls.
  • the invention has for its object to develop the above-mentioned transmission so that the above-mentioned disadvantages are avoided and in addition a simple mounting option of the transmission is achieved.
  • the invention therefore essentially consists in forming the ring gear provided in the overload clutch from plastic and arranging a protective plate, preferably a metallic cam disk, between the ring gear and the spring device.
  • a protective plate preferably a metallic cam disk
  • the material of the protective plate must have greater mechanical stability and strength than the ring gear.
  • the protective plate or cam disc is, according to the invention, non-rotatably connected to the ring gear, so that the compressive force of the spring can act axially on the end face of the ring gear via the protective plate or metallic cam disc and nevertheless the frictional forces occurring during the torque limitation directly on the protective plate or metallic Attack the cam disk.
  • the relatively soft end face of the ring gear made of plastic is effectively protected from abrasion or damage due to the slipping of the overload clutch.
  • Another advantage of the design of the transmission according to the invention is a quiet running noise.
  • the plastic gears of the epicyclic gear mesh with plastic teeth of the internal toothing of the ring gear and, in the event of overload, the plastic ring gear rubs against the inner wall of the gear housing, which is also made of plastic, whereby the same materials come into contact with one another.
  • the ring gear made of metal touches the metal gears of the epicyclic gear, so that a comparatively higher running noise than in the gear according to the invention occurs.
  • a further development of the invention provides that the protective plate or metallic cam disk releasably rests on the ring gear and is connected to it in a rotationally fixed manner.
  • the main advantage of this design is that when the protective plate or cam disc has worn off, the entire ring gear does not have to be replaced, but only the protective plate or cam disc has to be replaced.
  • the ring gear is provided on the end face with recesses and the protective plate or metallic cam disk with projections which fit into the recesses of the ring gear and hold the protective plate or cam disk non-slip in the circumferential direction with respect to the ring gear . This ensures that when the ring gear is at a standstill, that is to say during a torque transmission from the drive shaft to the output shaft below a predetermined torque load, the protective plate or cam disk also stands still. If, on the other hand, the ring gear begins to slip or turn when a predetermined torque load is exceeded, the protective plate or cam plate taken from the ring gear.
  • the metallic cam disk preferably consists of a deep-drawable and embossable metal, so that the cam disk can be produced in a simple manner by means of a stamping process.
  • the cam disc can therefore be designed as a simple stamped part, which makes production much easier.
  • the ring gear according to the invention consists of an injection-moldable thermoplastic which has sufficient mechanical stability.
  • a polyamide 6.6 with mineral filling can be provided as the injection-moldable thermoplastic.
  • a particularly assembly-friendly design of the gear provides a spring device in the form of a compression spring 18 which exerts axial pressure on the metallic cam disk and thus the ring gear via a fixed pressure ring.
  • the cam disk and the pressure ring lie flat against one another.
  • the opposing surfaces of the thrust washer and the cam ring are provided with wedging elements, preferably lugs distributed in a ring on the thrust ring or the cam disc.
  • the pressure ring like the metallic cam ring, preferably consists of a deep-drawable and embossable metal, so that it can also be produced in a simple manner by stamping from a metal plate.
  • the epicyclic gear has at least one planet gear meshing with the drive shaft and arranged on at least one planet carrier, the planet carrier in one a distal end of a drilling spindle of the planet carrier area is formed with a bead-like reinforcement.
  • a reinforced design of the planet carrier allows the predetermined torque load to be increased without the planet carrier or the drilling spindle of the planet carrier breaking during operation. This allows greater torque transmission from the drive shaft to the output shaft without the overload clutch having to respond.
  • the epicyclic gear is designed in two stages, each with different gear ratios, and the ring gear is provided with an internal toothing adapted to both stages. This enables a variable reduction of the gearbox with different torque loads.
  • the gear housing has a cylindrical inner wall for receiving the ring gear, the inner wall being partially conical.
  • the mutually parallel sections of the inner wall serve for good guidance and a good later fit of the ring gear within the gear housing during assembly of the transmission according to the invention, while lubricant absorption is possible due to the gaps formed between the conical sections of the inner wall and the ring gear.
  • the gear housing which is usually made of plastic, is easier to remove from its mold due to the conical sections of its inner wall.
  • the transmission according to the invention is preferably suitable for use in an accumulator-driven electric drilling or electric screwing tool. Because most of the for the gear provided components are made of plastic, such an accumulator gear electric drilling or screwing tool is characterized by a relatively low weight. In comparison to the previously known accumulator-driven electric drilling or screwing tools, this weight is further reduced by using a ring gear made of plastic.
  • the drive unit for a cordless screwdriver is shown.
  • the drive unit has an electric motor 22 with a drive shaft 23 projecting into a transmission housing 4.
  • a motor flange 7 is screwed on by means of cylinder screws 21.
  • Snap connections for holding the transmission housing 4 are preferably arranged on this motor flange 7.
  • An epicyclic gear is arranged within the gear housing 4 in order to achieve a speed reduction from the drive shaft 23 of the electric motor 22 to an output shaft 24.
  • the drive shaft 23 and the output shaft 24 lie on a common axis A.
  • a suitable screw chuck is fastened to the output shaft 24 for the sake of clarity and not shown in FIG.
  • the gear housing 4 is of cylindrical design, the gear housing having a larger diameter in the front region 4a assigned to the drive shaft 23 than in a rear region 4b which is assigned to the output shaft 24.
  • the already mentioned epicyclic gear in the form of a two-stage planetary gear is contained in the front area 4a within the gear housing 4.
  • This two-stage planetary gear has a first planet carrier 1 with three drilling spindles 1a pointing in the direction of the electric motor 22 and a planet carrier web 1b, the axis of the planet carrier web being collinear with the axis of the drive or output axis A.
  • On the drilling spindles 1a of the first Planet carriers 1 are each rotatably mounted on planet wheels 8, preferably made of plastic, which mesh with a motor pinion 10 arranged on the drive shaft 23 of the electric motor 22.
  • the first planet carrier 1 can in principle be equipped with only one drilling spindle 1a, it is advisable to provide several, preferably three, drilling spindles 1a offset from one another by 120 ° for reasons of better synchronization.
  • the planetary gear also has a second planet carrier 2 with preferably three drilling spindles 2a.
  • the planet carrier web 2b of this second planet carrier 2 is rotatably connected to the output shaft 24.
  • second planet gears 9 are rotatably fitted, which mesh with teeth mounted on the planet carrier web 1b of the first planet carrier 1.
  • the translation of the two stages of the planetary gear shown in FIG. 1 can be selected, for example, such that the basic ratio of the first stage is 6: 1 and the basic ratio of the second stage is 4.8: 1.
  • a torque limiting device in the form of an overload clutch is provided to adapt the cordless screwdriver to different loads.
  • this consists of a cylindrical ring gear 3, a metallic cam disk 5, a metallic pressure piece 6 and a compression spring 18 designed as a spiral spring.
  • This made of plastic, for example made of polyamide 6.6 with mineral filling the existing ring gear 3 sits within the gear housing 4 and is provided with a stepped internal toothing, so that the planet gears 8 of the first stage and the planet gears 9 of the second stage of the planetary gear are in engagement with the respective internal toothing of the ring gear 3.
  • the ring gear 3 is pressed by axial pressure of the compression spring 18 via the pressure piece 6 and the cam ring 5 against a stop wall 12, which is arranged here in the gear housing 4 on the motor flange 7, here a stop disk made of metal.
  • This contact pressure is adjustable by an adjusting ring 16 by an operator of the cordless screwdriver.
  • the prestress of the compression spring 18 can be adjusted by means of a curve located within the rotary ring 16.
  • the ring gear 3 is thus pressed onto the stop wall 12 with a pressure exerted by the compression spring 18 via the pressure piece 6 and the cam ring 5.
  • the ring gear 3 is fixed until the torque load on the cordless screwdriver exceeds the frictional force. If the torque load exceeds this value, the ring gear 3 slips and begins to rotate. An effective torque limitation of the transmission according to the invention is thus achieved and thus a screw is tightened up to a predetermined torque.
  • the drive shaft 24 is surrounded in the rear region 46 of the gear housing 4 by a spindle bearing 11, on its end face in the direction
  • Output shaft 24 is connected to a ball cage 13 and an axial disk 14 with a shaft retaining ring 19.
  • the above-mentioned adjusting ring 16 is covered on the end face with a cover disk 17 and held by screws 20 on the gear housing 4.
  • a spring clamping ring 15 is arranged between the compression spring 18 and the adjusting ring 16.
  • ring gear 3 the metallic cam 5, the pressure ring 6 and the compression spring 18 is shown in an exploded view.
  • the ring gear 3 provided with an internal toothing 26 is provided on the side of the metallic cam disk 5 with recesses 27 into which the projections 28 of the cam disk 5 engage, so that the cam disk 5 is connected in a rotationally fixed manner to the ring gear 3 in the assembled state.
  • the cam ring 5 and the pressure ring 6 are preferably formed as stamped parts and have wedging elements 30, 31 on the opposing surfaces. These wedging elements 30, 31 are designed in the illustration in FIG. 2 as projecting lugs 31 and 30 formed in a ring on the cam ring 5 and pressure ring 6, respectively.
  • cam ring 5 and pressure ring 6 is not limited to the embodiment shown in FIG. 2. Rather, other configurations of cam ring 5 and pressure piece 6 can also be provided. For example, trough-like depressions can be provided on the side of the cam disk 5, which lies opposite the pressure ring 6, and spherical elevations on the opposite side of the pressure ring 6. In the simplest case, neither the cam ring 5 nor the pressure ring 6 has wedging elements. However, slipping occurs even at low torque loads.
  • At least one of the drilling spindles 1a, 2a of the planet carrier 1, 2 is formed with a bead-like reinforcement 33 at its area opposite the distal end, i.e. on the radial carrier part of the planet carrier 1, 2 .
  • FIG. 3 shows the planet carrier 2 of the transmission shown in FIG. 1 with drilling spindles 2a and planet carrier web 2b.
  • the drilling spindles 2a are reinforced at their base in that the drilling spindles 2a have bead-like reinforcements 33.
  • Such a design of the planet carriers 1, 2 serves to mechanically stiffen the planet carriers 1 and 2 and thus to improve their durability. Breaking of the drilling spindles 2a can thus be effectively avoided even with high torque loads.
  • these bead-like reinforcements 33 are polished on their surface in order to remove microcracks during manufacture.
  • the gear housing 4 of FIG. 1 preferably has a cylindrical inner wall.
  • the inner wall of the gear housing 4 is partially conical, so that, starting from the motor flange 12 in the direction of the cam disk 5, an increasing gap is formed between the outer ring gear wall and the inner wall of the gear housing, so that an optimal lubricant deposit is available.
  • the gear housing 4 can have, for example, four conical wall sections arranged in a ring-like manner with respect to one another, which are interrupted by wall sections which have a constant inner diameter. This partially conical design of the inner wall of the gear housing 4 is shown in dashed lines in Fig. 1 on the lower wall.
  • cam disc can also consist of other materials, provided that the material has sufficient mechanical strength.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
  • Gears, Cams (AREA)
EP94110238A 1993-07-23 1994-07-01 Transmission à trains épicycloidaux équipée d'un limitateur de couple et son application dans des outils à main Expired - Lifetime EP0635658B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4324876 1993-07-23
DE4324876A DE4324876C2 (de) 1993-07-23 1993-07-23 Getriebe und dessen Verwendung

Publications (3)

Publication Number Publication Date
EP0635658A2 true EP0635658A2 (fr) 1995-01-25
EP0635658A3 EP0635658A3 (fr) 1995-03-29
EP0635658B1 EP0635658B1 (fr) 1999-01-13

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Application Number Title Priority Date Filing Date
EP94110238A Expired - Lifetime EP0635658B1 (fr) 1993-07-23 1994-07-01 Transmission à trains épicycloidaux équipée d'un limitateur de couple et son application dans des outils à main

Country Status (3)

Country Link
US (1) US5551927A (fr)
EP (1) EP0635658B1 (fr)
DE (4) DE9320533U1 (fr)

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DE19729988C1 (de) * 1997-07-12 1998-08-13 Buehler Gmbh Nachf Geb Formschlüssige Verbindung zwischen einem aus Kunststoff bestehenden Getriebegehäuseteil und einer Adapterplatte eines Elektromotors
EP2228157A1 (fr) * 2009-03-13 2010-09-15 Metabowerke GmbH Visseuse ou perceuse entraînée de manière électromotrice
CN102852998A (zh) * 2011-06-28 2013-01-02 吴江市德菱电梯配套有限公司 一种过载离合器
CN103939587A (zh) * 2013-01-23 2014-07-23 博世汽车部件(长沙)有限公司 车辆起动机及其过载保护和减振装置

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DE19615002A1 (de) 1996-04-16 1997-10-23 Mekra Lang Gmbh & Co Kg Getriebe-Einheit
DE19700292C2 (de) * 1997-01-08 2000-04-13 Ims Morat Soehne Gmbh Schaltbares 2-Gang-Getriebe
DE19815999B4 (de) * 1997-08-25 2006-03-16 Ktr Kupplungstechnik Gmbh Überlastkupplung mit an Außen- und Innenumfang vorgesehenen Materialaussparungen
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AT407737B (de) * 1999-06-24 2001-05-25 Johannes Buchner Antriebsvorrichtung für ein fahrrad
DE10047308A1 (de) * 2000-09-25 2002-05-02 Ims Morat Soehne Gmbh Zweistufige Getriebeanordnung
US6676557B2 (en) * 2001-01-23 2004-01-13 Black & Decker Inc. First stage clutch
US7101300B2 (en) 2001-01-23 2006-09-05 Black & Decker Inc. Multispeed power tool transmission
DE10201141B4 (de) 2002-01-15 2009-10-15 Pierburg Gmbh Stellgetriebe mit Einrichtungen zur Feststellung der Abweichung von einer vorgegebenen Ausgangsstellung
US7066691B2 (en) * 2002-01-25 2006-06-27 Black & Decker Inc. Power drill/driver
DE10346403B4 (de) 2003-10-07 2007-05-10 Pierburg Gmbh Stellvorrichtung
FR2861911B1 (fr) * 2003-10-29 2007-03-16 Denis Palanque Dispositif motorise pour l'entrainement en rotation d'une piece mecanique
US7314097B2 (en) * 2005-02-24 2008-01-01 Black & Decker Inc. Hammer drill with a mode changeover mechanism
US7469753B2 (en) 2005-06-01 2008-12-30 Milwaukee Electric Tool Corporation Power tool, drive assembly, and method of operating the same
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DE102005041698B4 (de) * 2005-09-02 2009-02-05 Micromotion Gmbh Getriebeeinheit, insbesondere Mikro-Getriebeeinheit
US7980324B2 (en) 2006-02-03 2011-07-19 Black & Decker Inc. Housing and gearbox for drill or driver
DE102006025538A1 (de) * 2006-06-01 2007-12-06 Metabowerke Gmbh Elektrohandwerkzeuggerät
CA2610045A1 (fr) * 2007-11-07 2009-05-07 Marcel Durand Transmission a engrenages planetaires pour un systeme moteur
US20100105514A1 (en) * 2008-10-28 2010-04-29 Caterpillar Inc. Drive Assembly having ring gear friction clutch
US8251158B2 (en) 2008-11-08 2012-08-28 Black & Decker Inc. Multi-speed power tool transmission with alternative ring gear configuration
DE102009054931A1 (de) * 2009-12-18 2011-06-22 Robert Bosch GmbH, 70469 Handgeführtes Elektrowerkzeug mit einer Drehmomentkupplung
US8584770B2 (en) 2010-03-23 2013-11-19 Black & Decker Inc. Spindle bearing arrangement for a power tool
CN103402707B (zh) * 2011-03-11 2016-06-22 S·D·温纳德 手持式驱动装置
DE102011102731B4 (de) * 2011-05-20 2013-10-31 Ims Gear Gmbh Planetengetriebe mit verbessertem Planetenträger und dessen Verwendung
EP2602504B1 (fr) * 2011-12-09 2014-05-21 Robert Bosch GmbH Embrayage de protection
CN103115124B (zh) * 2013-03-04 2015-06-17 宁波新宏液压有限公司 一种具有离合装置的行星齿轮减速机
WO2016143370A1 (fr) * 2015-03-09 2016-09-15 株式会社エクセディ Dispositif d'embrayage
DE102015206933A1 (de) * 2015-04-16 2016-10-20 Bühler Motor GmbH Getriebemotor
CN108626326B (zh) * 2018-06-21 2023-11-14 浙江明磊锂能源科技股份有限公司 一种齿轮箱及带有该齿轮箱的电动工具
CN109838528B (zh) * 2019-03-29 2021-12-03 伊蒙妮莎（常州）发电设备有限公司 一种用于柴油发电机的可双向离合扭矩限制脱扣器

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DE19729988C1 (de) * 1997-07-12 1998-08-13 Buehler Gmbh Nachf Geb Formschlüssige Verbindung zwischen einem aus Kunststoff bestehenden Getriebegehäuseteil und einer Adapterplatte eines Elektromotors
EP2228157A1 (fr) * 2009-03-13 2010-09-15 Metabowerke GmbH Visseuse ou perceuse entraînée de manière électromotrice
CN102852998A (zh) * 2011-06-28 2013-01-02 吴江市德菱电梯配套有限公司 一种过载离合器
CN103939587A (zh) * 2013-01-23 2014-07-23 博世汽车部件(长沙)有限公司 车辆起动机及其过载保护和减振装置
CN103939587B (zh) * 2013-01-23 2017-06-23 博世汽车部件(长沙)有限公司 车辆起动机及其过载保护和减振装置

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Publication number Publication date
DE4433584A1 (de) 1996-03-28
DE9320533U1 (de) 1994-09-22
DE4324876A1 (de) 1995-02-02
EP0635658A3 (fr) 1995-03-29
DE59407629D1 (de) 1999-02-25
US5551927A (en) 1996-09-03
DE4324876C2 (de) 1995-06-01
EP0635658B1 (fr) 1999-01-13
DE4433584C2 (de) 1998-08-27

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